Wire tying mechanism



June 27, 1950 M. H. TUFT WIRE mus mzcmmxsm 4 Sheets-Sheet 1 Filed May 19, 1945 nun-F.-

FIG. 2

INVENTOR.

MILES H. TUFT ATTORNEYS June 27, 1950 M. H. TUFT 2,512,754

WIRE TYING MECHANISM Filed May 19, 1945 4 Sheets-Sheet 2 22s 2|? u is? In l INVENTOR.

MILES H. TUFT ATTORNEYS June 27, 1950 M. H. TUFT 2,512,754

WIRE TYING MECHANISM Filed May 19, 1945 4 Sheets-Sheet 3 ATTORNEYS June 27, 1959 M. H. TUFT WIRE TYING MECHANISM 4 Sheets-Sheet 4 Filed May 19, 1945 INVENTOR. MILES H. TLFT ATTORNEYS Patented June 27,1950

UNITED STATES PATENT OFFICE 2,512,154 wmrirrmc MECHANISM Iowa Application May 19, 1945, Serial No. 594,684

26 Claims. (Cl. 140-93) The present invention relates generally to wire tying mechanism, with particular reference to mechanism of the type used on agricultural baling presses which gather from the field a crop of material, such as hay, straw, or the like, and then press and automatically tie the material into bales, and finally discharge the bales from the end of the bale case.

The principal object of my invention relates to the provision of a novel and improved wire tying mechanism, which can be used for tying hay bales or for any other appropriate use, and which ties the wires more securely and more efficiently, but which is at the same time simple in construction and inexpensive to manufacture.

Wire tying mechanisms which tie two wire sections together by twisting, are well known to 2 These and other objects and advantages of my invention will be apparent to those skilled in the art after a consideration of the following description, in which reference is had to the drawings appended hereto, in whichr Figure 1 is a plan view ofa. wire tying mechanism embodying the principles of my invention.

Figure 2 is a sectional elevational view of a portion of the top of the bale case, taken along the line 2-2 in Figure 1 and showing the timing mechanism which initiates the action of the wire tying mechanism after the bale of predetermined length has been accumulated.

Figure 3 is an elevational view of the wire tying mechanism, drawn to a smaller scale, with a portion of the side wall of the bale case broken away t seskilled in the art, but I have found thatr wires which are merely twisted together do not hold securely when tension is applied to the wires, but tend to untwist and pull apart. I have discovered, however, that when the twisted portion of a pair of wires is bent or kinked after the twisting operation, the strength of the twisted joint is greatly increased, for when tension is applied to a kinked joint, the latter tends to kink even more tightly, and usually the wire will break before the joint becomes untwisted.

It is, therefore, a further object of my invention to provide means for applying a bend or kink to the wire sections after they have been twisted together.

Still another object relates to the provision of suitabletiming and actuating means for synchronizing movements of the needle, the wire twisting mechanism, and the bending or kinking mechanism. Inasmuch as the kinking operation must be performed after the twisting is completed, it is evident that the needle holding the wire must be held stationary in tying position for a sufficient interval to permit the twisting and kinking operations to be performed. Therefore, a further object of my invention relates to the provision of needle driving mechanism which provides for such an interval of time in which the needle is held stationary.

Another object relates to the provision of a wire tying mechanism which twists two wire sections together, then severs the twisted portion near the center of the latter and bends or kinks the a two parts of the severed twisted portion. A related object has to do with the provision of a combined cutting and kinking mechanism which is operative after the twisting mechanism has completed its operation.

to show the construction of the plunger.

Figure 4 is an elevational view, drawn to an enlarged scale, of ,the twisting and kinking mechanism, as viewed along the line 4-4 in Figure 1, at the instant that the needle has brought the wire into tying position but before any tying action has taken place.

Figure 5 is a bottom plan view of one of the twisting and kinking assemblies, drawn to a slightly larger scale than Figure 4.

Figure 6 is a view similar to Figure 5 but showing the position of the part in the stage of operation after the wire has been twisted and severed and partly kinked.

Figure '7 is an elevational view taken along a line 'l'| in Figure 1, showing the timing and actuating mechanism.

Figure 8 is a sectional view taken along a line 88 in Figure 1 and showing the means for driving the kinking and twisting mechanism.

Figure 9 is a sectional elevational view taken along a line 9-9 in Figure 1 and showing one of the wire containers.

Figure 10 is a plan view of a pair of the wire containers, one of the latter being shown in section, as taken along a line Ill-l0 in Figure 9.

Figure 11 is a sectional elevational view taken along a line ll-|| in Figure l and showing the casing for the wire tying mechanism.

Figure 12 is a partially assembled view of the wire tying mechanism.

Figure 13 is a sectional elevational view taken along a line |3--l3 in Figure 12 and Figures 14 and 15 show the two completed joints after the wire sections have been twisted together, severed, and kinked.

Referring now to the drawings, the baling press is indicated in its entirety by reference numeral 20 and comprises a long rectangular 3 bale case 2|, within which is slidably disposed a reciprocating head or plunger 22. The bale case 2| comprises four longitudinally extending angle members 23 which form the four corners of the bale case and which support the side walls 24, the top wall 25 and the bottom plate 28. Inasmuch as the baler, with its pickup mechanism is not a part of the present invention, all descniption thereof is omitted for the sake of simplicity/for the wire tying mechanism which constitutes the present invention can be used with any conventional baling apparatus, except as hereinafter described. It is suiilcient to say that the plunger 22 slides through the bale case from right to left to compres the hay or other material into a bale, the length of which is indicated by the broken line B. When the bale acquires the predetermined length B, as measured by a serrated measuring wheel 26, the latter initiates the operation of wire tying mech anism indicated in its entirety by the reference numeral 21, which securely binds the bale with a pair of baling wires. The forming of a new bale pushes the completed bale toward the left as viewed in Figures 1 and 3, which accomplishes discharging of the completed bales from the discharge end (not shown) at the left hand end of the bale case.

Cooperating with the tying mechanism 21 isa pair of needles 36, which are rigidly fixed by clamps 3| in laterally spaced relation on a ball 32, which extends transversely beneath the bale case 2| and which is provided with a, pair of upwardly extending arms 33 pivotally connected by a pair of coaxially disposed trunnions 34 to brackets 35 fixed to the two side walls 24 of the bale case, respectively. In Figure 3, the needles 36 and their supporting arms 33 are shown in solid lines in their inactive position with the needles retracted from the bale case 2|, and in dotted lines in their tying position, with the needles 36 inserted through the bale case into tying position in cooperative relation with the tying mechanism 21.

The wire tying mechanism 21 comprises a casing 46 consisting of two casing sections 4|, 42 assembled by bolts 43 and supported on a pair of mounting plates 44 at opposite ends, respectively, of the casing 46, by means of bolts 45. The mounting plates 44 are suitably fixed, as by bolting, to the top of the bale case 2|.

Disposed within the casing 46 is a main drive gear 46 (see Figur 12). 'The drive gear 46 is mounted on a drive shaft 41 and is fixed thereto by means of ,a suitable key 46. The drive shaft 41 is journaled in a pair of bearings 49, 56, preferably cast integrally with the two casing sections 4|, 42, respectively. The drive shaft 41 is secured against axial movement relative to the casing 46 by means of a pair of cotter pins inserted through suitable radial apertures in the shaft 41 adjacent the ends of the bearings 49, 56.

A pair of twister gears 53 are disposed on diametrically opposite sides of the main drive gear 46, respectively, in mesh with the latter. In Fi ure 12, the left hand gear has been removed. Each of the twister gears 53 is disposed within a gear chamber 54, formed in a lateral extension 55 of the casing 46. The diameter of each of the chambers 54 is made to slidably receive the ends of the associated twister gear 53, so that the gear 53 is centered and supported within the chamber 54 by means of the ends of the gear teeth, since the twister gears 53 are not provided with supporting shafts. Each of the gears 53 is i provided with a radially extending slot 56, which extends from the axis of rotation at the center of the gear 53, radially outwardly between a pair of gear teeth, which define an outwardly flaring opening to the slot 56, through which the wires can be shifted. The width of the slot 56 at the center of the gear 53 is sufiicient to receive a section of baling wire when the latter is shifted radially into the slot, but the slot is not wide enough for two sections of wire to pass each other in the slot; and, therefore, when two wires are placed within the slot 56 and the gear is rotated about its axis, the two pieces of wire are twisted together.

Normally, the slot 56 opens downwardly in register with a corresponding slot 51 in the bottom of the housing extension 55. The slot 51 communicates with the gear chamber 54 and extends upwardly on each side of the latter, where it is flared into an enlarged opening 58, as best shown in Figures 1 1 and 12. In Figure 12, the casing 46 is shown with the section 4| removed, to show the interior of the casing, and the twister gear 53 on the left side is removed to show the gear chamber 54 together with its slot 51 and enlarged opening 58.

Disposed within each of the enlarged openings 58 is a pair of bending or kinking members 66, 6|, each of which members comprises a shaft journaled in a corresponding passage 62, 63, in the housing sections 4|, 42, respectively (see Figure 13). The kinker shafts extend through gear chambers 64, 65 in the upper portions of the housing extension 55, the two chambers 64, 65 being disposed in communication with each other to receive a. pair of intermeshing drive gears 66, 61, respectively, which are fixed to the kinker shafts 66, 6|. One of the kinkers 6| of each pair is extended upwardly through the top of the casing portion 55 and carries a drive gear 68, which is rigidly fixed thereto. Thus, by rotating the gears 66, each kinker BI is rotated and drives its other kinker 66 through the gears 66, 61, the two kinkers of each pair therefore moving in relai i vely opposite directions of rotation. One of the kinkers 66 of each pair is provided at its lower end with a slot 16, best shown in Figures 4, 5 and 11. The slot 16 extends diametrically across the end of the kinker 66 and is normally disposed in alignment with the slot 56 in the proximate twister gear 53, but the slot 16 is appreciably greater in width, not only to provide for receiving the two wire sections as they are shifted into the twister gear slot 56, but to provide sufficient room so that when the twister gear 53 rotates, the wire sections within the slot 16 can twist freely without interference from the kinker 66.

The other kinker 6| of each pair is provided with an enlarged head portion 1| at the lower end thereof, which is greater in diameter than the end of the first mentioned kinker 66. The head 1| is provided with a slot 12 in the end thereof, extending diametrically across the end of the headandibeing' ofsubstantially the same width as theslotlll. Normally, the slot 12 is disposed in alignment with the slots 10 and 56, and is adapted to receive the wire sections during the tying operation.

It will be noted that each of the twister gears 53 is provided with a centrally disposed recessed portion 13, best shown in Figure 4, on each side face of the gear. The head 1| of each kinker 6| is sufliciently large in diameter to bear against the side of the recessed portion 13 of the proximate ear 53. It is new. evidentthat vim; the twister tween the edges or the nears-,1; which is fr ctive to sever the twisted portion; of the wire sections. As indicated in Figures 5 andjgfijthe 6 slot 98 (Figure Q) in the bracket 98 permitting a limited amount of vertical adjustment of the bracket relative'to the casing 88.

[The upper wire 81 passes downwardly over the sheave 92 and under a lower sheave 99 mounted on a shaft I88journaled in the lower portion-for the bracket 94. The wire 81 then 5101; 12 broadens toward its inner end, as'indii cated in dotted lines at 15, and the inner portion of the slot at is disposed at a slight angle to the outer edges of the slot at 12. This has the result that, after the wire sections are twisted together and the kinkers begin to'rotate in the direction indicated by the arrows in Figure 6, the wire sections are not severed immediately but are left intact until the kinkers-have rotated through appreciable angles. therebytaking up any slack that is present and tightening the wires to facilitate shearing. Continued rotation of the kinkers 88, 8I causes the slots to be rotated, thereby bending or kinking the portions 18 of the twisted wire sections disposed in withtions 11 of the twisted portions outside of the slots in the kinkers. However, the smaller .diameter kinker 88 produces a second bend or kink in the twisted portion engaged therein, due to the fact that the portions 18 of the wires, which to rotate until they have moved through an angle of approximately 180 degrees, at which time they reverse thier direction and return to their original position as shown in Figure 5. During this return movement, the kinked wires are ejected downwardly from the slots 18, 12, this ejecting action being produced by beveled portions 88, 8| along those edges of the slots 18, 12 that'lead during the return movement, providing inclined camming surfaces which, when the kinkers are returned to their normal position, act to force the twisted portions 18 downwardly out of the slots. Thus, it is evident that during the kinking operation, the twisted wire sections bear against the shoulders 82 at the leading edges of the kinkers, over which the wires are bent, but when the kinkers are reversed the shoulders 82 do not bear against the wires, but rather the latter are engaged by the inclined beveled surfaces 88, 8I to force the wires out of the slot.

The wire for each bale tie is fed from a pair of coils of wire 85, 88 above and below the bale case 2I, respectively. Hence, since there are two bale ties applied to each bale, there are two upper wires 81 extending from two upper coils 85 and two spaced lower wires 88 extending from the two lower coils 88. Each of the coils 85, 88 is supported within a generally rectangular container 89, the details of which will be described later. Each container 89 is provided with a centrally disposed aperture in one side thereof, through which the wire is drawn. Each of the upper wires 81 extends longitudinally above the bale case 2I and over a suitably grooved sheave 92, rotatably mounted on a shaft 93 journaled in a bracket 94 (see Figures 1 and 4). The bracket 94 is secured by a bolt 95 to a lug 98 cast integrally with the casing section 42, each lug 9'5 being apertured at 91 to receive the bolt 95 (see Figures 8 and 13). The bolt 95 passes through a in the slots 18, 12, angularly relative to the porpasses 'under'the extension of the casing 88, through the slot 12 in the combined cutter and kinker head 8|, thenthrough the slot 58 in the twister gearv 53, and through the slot 18 in the kinker 88. The three slots 12, 58 and 88 are disposed in alignment for this purpose and. the wire 81 extends longitudinally over the top of the bale from the slot 18 to a knot I85 (see Figure 3), at the upper left hand corner of the bale, by which the wire 81 is connected to the lower wire 88.

The lower wire 88 is drawn from the coil 88 in the container89 beneath the bale case 2| and extends around a grooved sheave I88 'joumaled on a bracket I81 that is bolted to the under side of the bale case 2I. The wire 88 extends downwardly from the sheave I88 and under another sheave I88 vjournaled at thelower end of the wire 88 extends upwardly along the needle 38 and overa pair of grooved sheaves I89, II8, which are journaled in the upper end of the needle 38 on a pair of fingers I I I, I'I'2,*res'pectively, projecting upwardly at the upper end of the needle. The need1e38 itselfcomprises a pair of spaced plate members 38' (see Figure 4), between which the sheaves I88, I89 and H8 are journaled. The upper ends of the finger I I I are interconnected above the sheave I'89 by an interconnecting strap II3, which prevents the wire 88 from becoming disengaged from the sheaves I89, II8, the wire 88 extending longitudinally under the bale from the sheave H8 and upwardly along the far end of the bale to the knot I85.

The operation of the tying mechanism thus far described is as follows:

After the knot I is tied at the time of securing the previous bale, the wires 81, 88 extend downwardly from the tying mechanism 21 through the bale case 2I to the needle 38. The plunger 22 forces the hay or other crop material against the end of the previously formed bale, gradually increasing the size of the bale being formed, and forcing the latter and also the previous bale toward the left (as viewed in Figure 3). Inasmuch as the wires 81, 88 extend downwardly between the bales they are forced along the bale case with the bales, drawing the wires out of the coils 85, 88 as the bale is formed. When the bale reaches the predetermined length, as measured by the measuring wheel 26, the tying mechanism is set into action by tripping mechanism which will be described later, causing the needle supporting bail 32 to swing upwardly in a counter cldckwise direction (as viewed in Figure 3) about the pivot 34, to the tying position as indicated in dotted lines in, Figure 3. In the tying position, as indicated in Figure 4, the needle 38 is in a position in which the two sheaves I89, II8 are brought to opposite ends of the aligned slots 18, 55, 12, thereby sliding the lower wire 88, which extends between the sheaves I89, II8, upwardly through the slot 51 in the casing portion 55, and into the aligned slots directly under the upper wire 81 in the twister gear slot 58. By means which will be described later, the twister gear 53 is then rotated, preferably three revolutions, thereby twisting the two wire sections 81, 88 together, in view of the fact that the slot 56 is so narrow that it prevents the two wires from passing each other within the slot. However, the slots 10,12 in the kinkers 60, 6| are broad enough to permit the wire to twist without interference, whereby the wire is twisted together three times between the two sheaves I09, II 0, thereby producing three twists on each side of the twister gear 53, in each of the slots 10, 12.

The twister gear 53 then stops rotating and the two kinkers 60, 6| are then rotated through an angle of approximately 180 degrees about their vertical axes. This movement of the head 1I relative to the twister gear 53 produces a shea ing action between the leading edge of the sl t 12 and the edge of the slot 56, shearing the twisted portion of the two wire sections at the right hand end of the slot 56 (as viewed in, Figures and 6). Further rotation of the kinkers causes the latter to bend or kink the severed twisted portions of the wires, and after a movement of 180 degrees as mentioned above, the kinkers 60, 6I reverse their direction and return to their original position thereby causing the inclined camming surfaces 80, 81 to push the kinked knot downwardly out of the slots 10, 12. Obviously, the bale tie is now completed and is completely free from the upper and lower wires 81, 88 which extend from the wire coils 85, 86, but the latter wires are tied together by that portion of the knot which is severedat the right side of the twister gear 53 (as viewed in Figure 4). Thus, a new bale is started by subsequent reciprocation of the plunger head 22; but, before the first stroke of the plunger, the needle 30 is withdrawn from the bale case.

It is necessary to accurately synchronize the movement of the needle 30 with the movement of the plunger 22 in order that there will be no interference between them which would cause damage to the needle or otherparts of the mechanism. Obviously, it is necessary that the needle be inserted through the bale case at a time when there is no hay in the path of the needle, for otherwise the hay would be gathered on the end of the needle and forced into the slot in the twister gear and kinkers. This is accomplished by providing vertically extending slots 5 in the working face of the plunger 22, as best illustrated in Figures 1 and 3. The slots II5 are suiilciently large to permit passage upwardly of the two needles, 30, but these slots are also narrow enough that they do not accumulate crop material therein as the plunger compresses the material into the bale. Thus, the needle must be inserted through the bale case 2| during the short interval of time that the slots I I5 are in alignment with the path of the needle 30, and the upper end of the needle must pass through the upper wall of the bale case 2| into the tyingmechanism before the plunger has withdrawn from the path of the needle. By providing an extension on the lower edge of the plunger in the form of a block II6 (see Fig. 3), I have improved this situation by slightly increasing the amount of available time in which to move the needle through the bale case. The extension block H6 is also slotted in line with the plunger head slots II5, so that loose hay moving over the needles ahead of the main portion of the plunger head 22 is pushed aside, thereby permitting the needles to be started on their movement across the bale case slightly earlier than if the extension block was not present. By starting the upward movement of the needle slightly earlier, the upper end of the same reaches the top of the bale case before the plunger 22 has withdrawn from the needle.

The entire wire tying mechanism, including the twister gearE the kinkers, and the needles, is actuated by power transmitted through a shaft I20, which extends transversely across the top of the bale case 2I and is journaled at one end in a bearing I2I mounted on standards I22 bolted to the top of the bale case, and which is journaled at the other end in a bearing I23, which is supported on avertically disposed longitudinally extending supporting plate I24 having a horizontal flange I25 which is fixed to the top of the bale case 2|. A pair of crank arms I26 are fixed to the opposite ends of the shaft I20, respectively, the outer end of each of the arms I26 being connected with the legs 33 of the bail member 32 by means of a link member I21 in the form of a helical tension spring. Each end of the spring I21 is provided with a fitting I28 attached thereto, which is journaled on a pivot or crank pin I29. One of the crank pins I29 is fixed to the outer end of the crank arm I26 and the other pivot pin is secured to a lug I30 fixed to the needle supporting arm 33. Thus, one revolution of the shaft I20 swings the crank arms I26 at each end thereof in a complete revolution, which acts through the spring links I21 to raise and lower the needle supporting arms 33, thereby causing the needles 30 to be moved upwardly through the bale case 2| and returned to their inactive position. Obviously, however, the needles 30 must be held in tying position for a sufficient interval of time to enable the twister gears 53 to rotate three revolutions and then oscillate the kinkers 180 degrees and return them to their original position. This interval of time in which the needles are held stationary is obtained by making the arms I26 and links I21 of such length and connected to the arms 33 in such a relation that the needles will be raised to their tying position appreciably before the shaft I20 has made one-half revolution. This position is indicated in dotted lines in Figure 3, in which the transverse portion of the bail 32 has en aged a resilient bumper or stop I35 on the bottomof the bale case. arm I26 of approximately degrees or less. Further rotation of the shaft I20 causes the arm I26 to stretch the spring I21, thereby holding the bail 32 against the stop I35 and thus holding the needles 30 in their tying position, while the shaft I20 makes approximately one-half revolution or slightly more, after which the needle supporting bail 32 is returned to the inactive position shown in Figure 3. This period of time in which the shaft I20 rotates through approximately degrees, with the, needle 30 in tying position, is ample for the tyin mechanism 21 to tie the knot, sever the twisted portion, and bend or kink the twisted end of the knot. The structure just described forms the subject matter of my co-pending application, Serial No. 701,574, filed October 5, 1946.

As explained herein before, the twister gears 53 are rotated three revolutions by turning the drive gear 46 through a single revolution, since the diameter of the latter is three times that of the twister gears 53. The diameter of the drive gear 46 also establishes the spacing between the two wires which bind each of the bales. The drive shaft 41 on which the drive gear 46 is mounted, is driven through a comparatively small beveled pinion I36, mounted on the shaft 41. The pinion I36 is adapted to mesh with a segment I31 This requires a. movement ofthe 9 of a beveled gear, the gear segment I31 being mounted on a disk I38 carried on a hub I39, which is rigidly fixed on the shaft I20 by means of a key I40 (see Figure 8) A hub I is fixed to the shaft 41 and is provided with a camming lobe I42, which slidably bears against the disk I38 during the first portion of the revolution of the shaft I20, preventing any rotation of the bevel gear I36 or drive shaft 41. Thus, during the first approximately 90 degrees of movement of the shaft I20, in which the needle is being raised to its tying position, the camming lobe I42 is sliding on the face of the disk I38 holding the beveled pinion I36 against rotation, but the disk I38 is cut away adjacent the gear segment I31, so that when the latter engages the beveled pinion I36, the camming lobe I42 is disengaged from the face of the diskand is free to rotate with the pinion I36. The gear segment I31 extends over approximately 90 degrees of the disk I38, and the relative diameters of the segment I31 and pinion I36 provides for exactly one revolution of the pinion I36 and shaft 41, whereupon the gear segment I31 upon further rotary movement of the disk I38 disengages the pinion I36, and at the same time the camming lobe I42 engages the disk I38 once more to hold the pinion I36 against further rotation.

As soon as the twister gears 53 have rotated three revolutions, and have stopped rotating, the kinkers are then actuated by means of a reciprocable member in the form of a rod I45, which is slidably supported in a bearing I46 for longitudinal sliding movement therein. The bearing I 46 is carried on a bracket I41, which is mounted on a post I48 cast integrally with a bearing member I49 in which the end of the shaft 41 is journaled. The bearing I49 is also cast integrally with a bearing I50 disposed perpendicular thereto, and which is journaled on the shaft I20 near the center thereof. The bracket I41 is in the form of a transverse strap member, which supports the sleeve I46 and also has a pair of twisted end portions I5I which are apertured to receive and slidably support the upper baling wires 81.

The reciprocable rod I45 is connected by means of a bolt I55 to a link I56 comprising upper and lower strap members, which are connected to a gear segment I51 by a pivot bolt I58. The gear segment I51 is provided with a hub I59, which is journaled on a vertical spindle I60, the latter being centrally disposed on top of the casing 40 of the wire tying mechanism. The gear segment I 51 might be made as a complete gear, disposed between the two kinker drive gears 68 in mesh with the latter at diametrically opposite sides of its periphery, but two sides of the gear I 51 are omitted, since only a few teeth are necessary in mesh with each of the gears 68 to rotate the latter substantially 180 degrees for actuating the kinkers. This is accomplished by means of a lug I6I attached to the disk member I38 on the side opposite the gear segment I31. The lug I6I engages the end of the reciprocating rod I45 at the time the gear segment I31 is disengaged from the beveled gear I36, pushing the rod I45 and link I56 toward the right as viewed in Figures 1 and 8. Force is thus transmitted to the gear segment I51 to shift the latter angularly in a counter clockwise direction as viewed in Figure 1, thereby twisting the kinkers through an angle of substantially 180 degrees. The lug I6I, upon continued rotation of the disk I38, disengages itself from the end of the rod I45, after which the latter is returned to its original position by means of a tension spring I62 connected to the bracket I41 and to the link I56 and stressed in tension when the lug I6I pushes the rod I45. When the spring I62 returns the rod and link I56 to its original position, the kinkers are reversed in rotation back to their original position with the slots 10, 12 in alignment with the twister gear slot 56. This position is determined by a stop collar I63 on the rod I45, which engages the end of the bearing sleeve I 46 to stop the'movement of the rod I45 toward the left as viewed in Figures 1 and 8. The position of the stop collar I63 on the rod I45 can be-adjusted by any suitable means to perfect the timing of the mechanism.

After the lug I6I disengages from the rod I45, the arm I26 has approached the path in its cycle in which the spring I21 is substantially closed, after which further movement downwardly of the arm I26 lowers the bail 32 to drop the needle 30 to its inactive position, which completes the tying cycle of the mechanism.

The power for turning the shaft I20 through one revolution to actuate the tying mechanism is transmitted through a one revolution, self-interrupting clutch device I10, the details of which are best shown in Figure '1. The clutch device I10 comprises a continuously rotating element "I having sprocket teeth I12 around the circumference thereof, and which is carried on a hub I13 (see Figure 1), journaled on the shaft I 20. The normally stationary element of the clutch mechanism comprises the shaft I20 and the arm I26 rigidly mounted thereon, which latter part lies over the open side of the normally rotating member IN. A clutch dog I11 is pivotally mounted on a pin I18 attached to the arm I26, and is in the form of a bell crank. one arm I19 of which carries a roller I80. The other arm I8I of the clutch dog I11 extends outwardly beyond the normally rotating member HI and engages a trip arm I82, which is' mounted on a shaft I83, the latter being rockably supported for movement about an axis parallel to the shaft I20 and spaced therefrom. Normally, the clutch member I1I is driven at a constant speed by a drive chain I84, which is trained around the sprocket teeth I12 and extends to a suitable drive sprocket (not shown), which is driven by the shaft which drives the plunger 22. An idler sprocket I is journaled on a bolt I86 which is secured in vertically adjusted osition in a slot I81 in the plate I24, for the purpose of adjusting the slack in the drive chain I 84 (see Figure '1). The chain I84 drives the sprocket I12 in a clockwise direction as viewed in Figure 7, and when the trip arm I82 is swung downwardly Or in a clockwise direction to disengage the arm I8I of the dog I11, the latter is turned in a clockwise direction about the mounting pin I18 by means of a spring I88 anchored to a pin I89 attached to the arm I26. The spring I8 rotates the roller I80 into engagement with an internal cylindrical track I90 inside the clutch member HI, and this track I90 has a hump or raised portion I9I which the roller I80 engages when it is rolling on the track I90. The rotating member I1I thus drives the arm I26 in a complete revolution, through the hump I9I, the roller I80, the dog I11, and the pin I18, thus actuating the wire tying mechanism as described above. During the rotation of the arm I26 and shaft I20, the trip arm I82 is' returned to its original position by means of a spring I9I con nected between a lug I 92 fixed to the arm I82 and a bolt I93 secured to the plate I24. The trip arm I82 is engaged in this position by the arm I8I of the dog I11, thereby rocking the latter to disengage the roller I80 from the hump I9I'. The clutch member I1 I is synchronized with the movement of the plunger 22 within the bale case, through the drive chain I84, so that the hump I9I' engages the dog III at the proper point in the cycle of the plunger 22, as explained above. Thus, it is evident that the trip arm I82 can be rocked at any time during the cycle of the baling plunger 22, without interfering with the timing of the wire tying mechanism.

The actuating shaft I20 is yieldably held in its normal inactive position by means of a locking collar I 95, which is sidable on the shaft I29 (see Figure 1), but is non-rotatablysecured thereto by means of a pin I96 fixed to the shaft I20 and engaging a slot I91 in the collar I95. The edge of the collar I95 is provided with an inclined camming surface I98, which bears against a com plementary. camming surface I99 in the adjacent edge of the-bearing HI, and the collar I95 is urged into engagement with the camming surface I99 by means of a coil spring 200 encircling the shaft I 20 and anchored to the latter by means of a pin 20I. When the trip arm I82 is rocked to disengage the dog I", the force transmitted through the chain I84 and hump I9I' to the roller I80 forces the camming surfaces I98, I99 apart against the action of the compression spring 200, thereby permitting the shaft {20 to rotate through a single revolution, but the camming surfaces I98, I99 engage once more at the time that the trip arm I82 engages the arm I8I of the dog I" to disconnect the roller I80 from the hump I9I'.

The shaft I83 extends through a sleeve 205, which is rotatable thereon, and the end of the shaft I83 is journaled in a bearing 206 in the form of an apertured plate secured to the top of the bale case. The opposite end of the shaft I83 is journaled within an aperture in the vertical plate I20. The sleeve 205 carries the serrated measuring wheel 26, which projects through a slot 201 in the top of the bale case, with the teeth of the wheel 28 in engagement with the bale being formed. A helical spring 208 is coiled about the wheel supporting sleeve 205 between a lug 209 welded to the sleeve 205 and a collar 2I0 fixed to the shaft I83 by a pin 2II. The collar 2I0 also serves as a thrust bearing at one end of the sleeve 205, the plate 206 acting against the opposite end of the sleeve 205. The end of the spring 208 nearest the wheel 29 is turned in an axial direction as indicated at 2I5 (Figure 1), in register with the lug 209, so that rotation of the wheel 25 rotates the lug 209 into engagement with the end 2I5 of the spring. The opposite end of the spring is extended tangentially outwardly and has an outer end 2I6 turned axially and is adapted to engage a trip plate 2" which is in the form of a bell crank having an inner arm 2I8 extending horizontally in a position in which it will be engaged by the outer end 2 I6 of the spring 208. The trip plate is secured to a supporting pin 2I9, which is journaled in an arm 220 of a casting which also has a hub 22I mounted on the shaft I83. The trip arm I82 is secured to the casting hub 22I by bolts 222. The trip plate 2" is urged in a clockwise direction (as viewed in Figure 2) by means of a coil spring 225, which acts in torsion between the casting arm 220 and the trip plate 2I'I and the latter is provided with a downwardly extending abutment 228, which engages the casting arm 220 to prevent any further movement in a clockwise direction from the position shown in Figure 2. The plate 2" can, however, be rotated in a counterclockwise direction, in order to tilt the arm 2I8 downwardly out of engagement with the end 2I5 of the spring 208. The trip plate 2" has an upwardly extending arm 221, the-outer edge 228 of which is inclined upwardly and outwardly overhanging the side wall 24 of the bale case 2 I, in the path of rotary sgvsinging movement of the needle actuating arm During the baling operation, the bales move toward the left as viewed in Figures 1 and 3. gradually rotating the measuring wheel 28 in a clockwise direction as viewed in Figures 3 and 7. thereby rotating the sleeve 205 relative to the shaft I83. By the time the wheel 28 has made nearly a complete revolution, the lug 209 on the sleeve 205 moves into engagement with one end 2I5 of the spring 208, while the other end 2I6 of the spring 208 moves into engagement with the arm 2! of the bell crank or trip plate 2I'I. Further rotation of the wheel 26 and sleeve 205 exerts a force through the lug 209, stressing the spring 208 in torsion between the lug 209 and the arm 2I8 and exerting a force against the trip plate 2II which tends to swing the arm I82 and shaft I83 in a clockwise direction as viewed in Figure 7, but this is resisted by the spring I9I which tends to hold the arm I82 in its holding position in engagement with the clutch dog arm I8I. Movement of the wheel 25, however, builds up a torsional stress in the spring 208 which finally overcomes the tension spring I9I, which causes the trip plate 2", shaft I 83, and arm I82 to swing in a clockwise direction (Figure 7), thereby disengaging the arm I82 from the clutch dog arm -I8I. The spring I88 then shifts the clutch dog I" to bring the roller I into contact with the inner track I90, which is on the constantly rotating member I1 I of the clutch, and when the hump I9I' engages the roller I80 the shaft I20 and arm I26 begin to rotate in a clockwise direction. The arm I25 swings upwardly, engaging the inclined surface 228 of the trip plate am 221, forcing the latter in a counterclockwise direction as viewed in Figure 2. This swings the spring engaging arm 2 I 8 downwardly, disconnecting it from the end 2I6 of the spring 208, thereby causing the latter to contract and snap past the engaging arm 2I8. The coil spring 225 immediately restores the trip plate 2 to its original position, with the lower arm 226 bearing against the casting arm 220, and the spring I9I returns the trip arm I82 into sliding engagement with the outside of the clutch housing III, where it is in a position to engage the arm I8I of the clutch dog II'I after the clutch has made a complete revolution, thereby disconnecting the roller I80 from the hump I9I on the constantly rotating member "I.

This action of the trip plate 2" and spring 208 insures that the tying mechanism will actuate only once, regardless of whether the measuring wheel 28 has any movement or not during the rotation of the clutch.

As explained before, two wires are tied around each of the bales, and each wire comprises two sections 81, 88 drawn from two coils 85, 86, respectively, above and below the bale case 2I. Each of the coils of wire is retained within a container 89, the details of which are more clearly shown in Figures 9 and 10 and which is claimed in my co-pending application, Serial No. 701,575, filed October 5, 1946. Each container 89 comprises two parts, one of which 230 is an open ended box having a pair of spaced side walls 28I,

m a top wall 23:, a bottom wall 234, and one a side wall 243, which is slidable along the side wall 232 of the box 233, while the end wall 242 is disposed perpendicular to the side wall 243 and serves to close the open end 240 of the box 238. The side wall 243 is provided with a centrally disposed circular aperture 244 and a slot 245, which extends horizontally from the aperture 244 to the end 246 of the wall 243. Thus, while the apertures 231 and 244 are disposed in register with drawn from the coil it bears against the rounded i mouth, which provides for feeding or dispensing the wire smoothly through the aperture 249 to prevent unduewear on either the wire or the inner edge of the aperture.

The outer end of the bottom wall 234 is provided with a pair of laterally spaced keyhole slots 255, which are adapted to receive a pair of tongues 251, turned upwardly from the fioor plate 258 on which the container is supported. At the opposite end of the box, the bottom wall is slotted inwardly at 259 to receive a lug 260, which is securely fixed, as by welding. to the floor plate 258. The end wall 242 of the other portion of the container is also provided with a slot 26l which is adapted to receive the lug 260. A securing pin 262 is inserted through suitable aligned apertures in the side walls 23l, 232 of the box 236, anaperture in the wall 243 of the container portion 2, and an aperture 263 in the lug 260. The pin 262 is readily removed from the apertures, thereby permitting the container to be removed from the supporting plate 258 by sliding it outwardly to detach the tongues 25'! from the keyhole slots 255.

In order to avoid the necessity for frequent shut down of the baler for the purpose of replacing the coils of wire, there are two containers 89, 89' for each wire section. Each of the containers 89, 89', is adapted to hold a coil of wire, and each pair of containers are supported side by side on the plate 258, with the bushing aperture of the second container 89' disposed in register with the aperture 236 in the side wall 23l of the container 89 from which the wire is being drawn. The two containers 89, 89' are identical in each pair, and are secured to a pair of identical spaced lugs 260, 260' by means of one long securing pin 262 having a cotter pin 265 for holding the pin 262 in place. Furthermore, the containers 89, 89 are interchangeable for the purpose which will be described.

During operation, the wire is fed from one end of the first coil in the container 89, the other end of this coil passing through the opposite opening 236 and is secured to the end of the second coil 85'. The two connected ends are preferably secured together by welding, so that they will pass through the wire tying mechanism without interference. The wire 81 is drawn through the bushing aperture 243 from the coil 85 until the latter is consumed, whereupon the wire will begin to feed from the second coil 85' in the second container 89', being drawn directly through the first container 89, since all of the central apertures 231, 249, 236 are in alignment. After the wire begins to feed from the second coil 85', a third coil of wire can be added as a new reserve coil. The pin 262 is then removed after it is released by removing the cotter pin 265, after which the container box 239 can be removed from the wire 81 by passing the latter through the aligned horizontal slots 238, 239. The other container portion 2 can also be removed by sliding the wire out through the slot 245 in the wall plate 243. The bushing 248 is provided with a slot 266, which extends from the central aperture 249 and communicates with the slot 245 in the wall plate 243. The slot 266 is preferably helical rather than straight, so that the wirewill not catch in this slot while it is being unwound from the coil, for the reason that the portion of the wire being unwound never takes a position parallel to the slot 266 and therefore does not fall into the latter, a it would if the slot 266 extended radially outwardly from the central aperture 249.

After the first container 89 has been removed, the second container 89 can be moved to the positoin prevoiusly occupied by the first container 89, so that the wire from the second coil 85 now feeds directly to the wire tying mechanism. A new coil of wire is now placed in the container 89 after its end has been welded to the end of the coil 85', and the two containers can then be secured to the plate 258 by the pin 262.

Iclaim:

1. In wire tying mechanism, the combination of a rotatable twisting member havin a radially extending slot therein for receiving two sections of wire and twisting them together by rotation of said member, and a cutting member disposed adjacent .said twisting member and rotatable about an axis substantially perpendicular to the axis of rotation of said twisting member, said cutting member having a cutting edge cooperable with an edge of said slot for severing said wire sections.

2. In wire tying mechanism, the combination of a rotatable twisting member having a radially extending slot therein for receiving two sections of wire and twisting them together by rotation of said member, and a rotatable kinker disposed adjacent said member and having a slot for receiving said sections of wire and rotatabf: for bending or kinking the twisted portion of said wire sections to condition the latter to resist separation under tension.

3. In wire-tying mechanism, the combination of a rotatable twisting member having a radially extending slot therein for receiving two sections of wire and twisting them together by rotation of said member, and a rotatable kinker disposed adjacent said member and having a slot for receiving said sections of wire, and means for rotating said kinker first in one direction to bend or kink the twisted portion of said. wires and then in the reverse direction to dislodge the wires from said, slot.

4. The combination set forth in claim 3 including the further provision that the edges of said kinker slot that lead when said kinker is reversed, are beveled to facilitate dislodging the kinked joint between the wires.

5. For use in baling apparatus, wire tying mechanism comprising in combination, a rotatable twisting member for receiving two sections of wire and twisting them together, cutting means for severing the twisted portion of said wire sections substantially midway between the ends of said twisted portion, a pair of kinkers disposed adjacent opposite sides 01 said twisting member and engageable with the severed twisted portions, respectively, for bending or kinking the latter, and means for successively rotating said twisting member, actuating said cutting means, and said kinkers.

6. In wire tying mechanism, the combination of a rotatable twisting member having a radially extending slot therein for receiving two sections of wire and twisting them together by rotation of said member, cutting means for severing the twisted portion of said wire sections substantially midway between the ends of said twisted portion, a pair of rotatable kinker disposed adjacent opposite sides of said twisting member and having slots therein aligned to receive said also serving to bend the severed twisted portion.

11. In wire tying mechanism, the combination of a rotatable twisting member having a radially extending slot therein for receiving two sections of wire and twisting them together by rotation of said member, a rotatable combined cutting member and kinker disposed adjacent said twisting member and having a slot normally aligned with said slotin the twisting member to receive said wire sections, and a cutting edge rotatable into shearing relation with said twisting member to sever the wire sections near the middle of the twisted portion thereof, a rotatable kinker disposed adjacent the twisting member on. the

wire sections, and means for rotating said kinkdeforming the twisted portion of the wire sections by the shifting movement of said cutting member, to condition the twisted portion to resist separation under tension.

'8. In wire tying mechanism, the combination of a rotatable twisting member for receiving two sections of wire and twisting them together, a

cutting member movable relative to said twisting member and cooperable with the latter to sever the wire sections adjacent said twisted portion, said cutting member being recessed to receive said twisted portion and movable beyond its cutting position to deform the severed twisted portion to condition the latter to resist separation under tension.

9. In wire tying mechanism, the combination of a rotatable twisting member having a radially extending slot therein for receiving two sections of wire and twisting them together by rotation of said member, a rotatable combined cutting member and kinker disposed adjacent said twisting member and having a slot normally aligned with said slot in the twisting member to receive said wire sections and a cutting edge rotatable into shearing relation with said twisting member to sever the wire sections adjacent said twisted portion, said cutting member being rotatable beyond its cutting position to bend or kink the severed twisted portion to condition the latter to resist separation under tension.

.10. In wire tying mechanism, the combination of a rotatable twisting member having a radially extending slot therein for receiving two sections of wire and twisting them together by rotation of said member, a rotatable combined cutting member. and kinker disposed adjacent said twisting member and having a slot normally aligned with said slot in the twisting member to receive said wire sections, the edges of said slots serving as cooperative shearing edges to sever the twisted wire sections when said cutting member is rotated to move said slots out of aligned position, the rotary movement of said cutting member opposite side thereof from said combined cutting member and kinker and having a slot normally aligned with said slots in said twisting and cutting members, and means for rotating said kinkers after said wire sections have been twisted together, to sever the twisted portion and bend or kink both of the severed parts to condition the latter to resist untwisting under tension.

12. The combination set forth in claim 11 including the further provision that the trailing edges of said slots in said kinkers with respect to said rotary movement thereof are beveled to serve as means for ejecting the twisted and kinked wire sections by reversing the direction of rotation of said kinkers.

13. In wire tying mechanism, the combination of a rotatable twisting member having a radially extending slot therein for receiving two sections oi wire and twisting them together by rotation of said member, a rotatable kinker disposed adiacent said member but spaced therefrom and having a slot normally substantially alined with the slot in said member, and means for rotating said kinker for moving the slot therein angularly out of alignment with the slot in said twisting member to bend that part of the twisted portion of the wire sections within said kinker slot angularly relative to that portion disposed in said slot in the member and angularly relative to the outer part of twisted wire portion beyond the opposite end of said kinker slot to form two bends or kinks in said twisted portion.

14. For use in baling apparatus, wire tying mechanism comprising in combination, means for twisting two wire sections together, a drive shaft connected with said twisting means for driving the latter and having a gear mounted thereon, cutting means for severing the wire sec- I tions adjacent the twisted portion, kinking means disposed adjacent said twisting means for kinking or bending said twisting means for kinking or bending said twisted portion, a reciprocative element connected with said cutting and kinking means for actuating the latter after the wire sections are twisted, and an actuating member so rotatable through a certain cycle for actuating I. Short connected with said rotatable mean and having a drive gear connected thereto, cutting means adjacent said twisting means for severing the wire sections near the midpoint of' the twisted portion thereof, kinking means disposed on each side'of said twisting means for kinking or bendingeach. severedpart of said twisted portion, a reciprocative element connected with said cutting-and kinking means for actuating the same after the wire sections are twisted, and an actuating member rotatable through a certain cycle for successively moving said needle to bring said wire sections together, rotating said 1 twisting means, reciprocating said element to actuate said cutting and kinking means, and retracting said needle.

16. The combination set forth imclaim including the further rovision that said rotatable ter being effective to stress said spring means,

said needle being retracted by the final portion of the revolution, which is also less than one half revolution.

1'1. The combination set forth in claim 15 including the further provision that said rotatable member includes a gear segment adapted to mesh with said ,drive gear driving a portion of a- 18. The combination set forth in claim 15 including the further provision that said rotatable member includes a gear segment adapted to mesh with said drive gear driving a portion of a revolution to drive said twisting means, and a lug on said rotatable member engageable with said reciprocative element after said gear segment has disengaged said gear, to reciprocate said element, thereby actuating said cutting and kinking means.

19. For use in baling apparatus, two wire tyin mechanisms, each of said mechanisms comprising in combination, a movable needle for bringing two wire sections together, a rotatable gear member having a radially extending slot for receiving said wire sections and twisting them together, cutting and kinking means disposed adjacent said twisting gear member for severing and kinking the twisted portionof the wire sections, gear means for actuating said cutting and kinking means, a single drive gear disposed between said two mechanisms and meshing with each of said twisting gear members associated therewith, a second drive gear disposed between said two mechanisms and meshing with each of said gear means associated with said cutting and kinking means, and means for transmitting power to said drive gears in timed sequence.

20. The combination set forth in claim 19, including the further provision that said power transmitting means includes a rotatable element having a gear segment attached thereto and a projection in predetermined spaced relation to said segment, a gear adapted to mesh with said gear segment during a portion of a revolution of said element, said gear being connected to drive said twisting means drive gear, and a reciprocative part connected with said second drive gear and engageable with said projection to actuate said cutting and kinking means immediately after said gear segment disengages from the gear as= sociated therewith. n

21. For use in baling apparatus, two wire tying 'mechanisms, each offsaid mechanisms comprising in=combination, a movable needle for bringing two wire sections together, a rotatable gear member having a radially extending slot for receiving said wire sections and twisting them together, a pair of kinkersrotatably disposed on opposite sides, respectively, of said twisting gear 7 and having recesses 'normallyaligned with said slot for receiving said wire sections, cutting means'on one of said kinkers for severing the twisted wire sections adjacent said twisting gear, and gear means for rotating said kinkers to turn said recesses out of alignment with said twisting gear slot to bend the severed twisted portions of the wire sections to condition the latter to resist untwisting under tension, a drive gear disposed between said two mechanisms, and meshing' with each of said twisting gear members as- 'sociated therewith, a second drive gear disposed between said two mechanisms and meshing with each of said gear means associated with said cutting and kinking means, and means for transmitting power to said drive gears in timed sequence.

22. The combination set forth in c1aim 21,

' including the further provision that said power transmitting means includes a rotatable element having a' gear segment attached thereto and a projection in predetermined spaced relation to said segment, a gear adapted to mesh with said gear segment during a portion of a, revolution of said element, said gear being connected to drive said twisting means drive gear, and a reciprocative part connected with said second drive gear and engageable with said projection to actuate said cutting and kinking means immediately after said gear segment disengages from the gear associated therewith.

23. The combination set forth in claim 21, in cluding the further provision that said power transmitting means includes a rotatable element having a gear segment attached thereto, a projection in predetermined spaced relation to said segment, means, connecting said element with said needle for moving the latter into tying position, a gear connected to said twisting means drive gear and adapted to mesh with said gear segment during a portion of a revolution of said element, and a reciprocative part connected with said second drive gear and engageable with said projection to actuate said cutting and kinking means immediately after said gear segment disengages from the gear associated therewith.

24. In wire tying mechanism, a casing, a main drive gear rotatably disposed therein, a twister gear disposed in said casing adapted to mesh with said drive gear, said twister gear having a radially extending slot therein for receiving a pair of wire sections to be twisted together, a pair of kinkers rotatably mounted in said casing on opposite sides of said twister gear, respectively, and having slots normally disposed in alignment with said gear slot, intermeshing gear means in said casing interconnecting said kinkers, and a drive gear connected with said kinkers for rotating the latter.

25. In wire tying mechanism, a casing, a large drive gear rotatably dis-posed therein, a pair of comparatively small twister gears disposed in said casing in mesh with said drive gear on opposite sides thereof, respectively, each of said twister gears having a radially extending slot therein for receiving wire sections to be twisted together, a pair or kinkers rotatably mounted in said casing on opposite sides of each of said twister gears, respectively, each of said kinkers comprising a shaft having its axis disposed substantially perpendicular to the axis of rotation of the twister gear associated therewith and having a wire reiving slot disposed in one end thereof, and

rmally in alignment with said twister gear slot, one of said kinkers of each pair being provided with a wire cutting edge along one edge of the slot cooperable with an edge 01' said twister gear slot for severing said wire sections by rotation of said kinker relative to said twisted gear, I

gear means interconnecting each pair of kinkers, actuating gears connected to said kinkers, and a common drive gear mounted on said casing in mesh with said actuating gears.

26. In wire tying mechanism, the combination of a rotatable twisting member having a radially extending slot therein for receiving two sections of wire and twisting them together by rotation of said member, a kinker member mounted for forward and reverse movement and having a slot to receive the twisted portions of the wire adjacent the twister member, and means for moving the kinker member first in one direction to bend or kink the twisted portions of the wire, and then in the reverse direction to eject the twisted and kinked portions from the slots in said members, the slot in the tinker member having inclined edges which lead in said reverse direction of rotation to provide the ejecting action.

' MILES H. TUFT.

. REFERENCES CITED The following references are of record in the file of this patent:

' UNITED STATES PATENTS Number Name "Date 143,376 Palmer Sept. 30, 1873 291,828 Young et al. Jan. 8, 1884 508,257 Suter Nov. 7, 1893 661,015 Kennedy et a1 Oct. 30, 1900 823,556 Smith June 19, 1906 827,229 Gibbs July 31, 1906 889,815 Schmid June 2, 1908 994,661 Schubert June 6, 1911 1,125,991 Emery Jan. 26, 1915 1,134,020 Showalter Mar. 30, 1915 1,243,570 Trigg Oct. 16, 1917 1,289,554 Schleicher Dec. 31, 1918 1,590,319 Robbins June 29, 1926 1,673,125 Robbins June 12, 1928 1,769,330 Bull July 1, 1930 1,836,593 Harvey Dec. 15, 1931 1,891,664 Brenizer Dec. 20, 1932 1,990,526 Claar et a1 Feb. 12, 1935 

